Locking device

ABSTRACT

A locking device especially adapted to secure relatively movable concentric members together. The device is particularly useful for locking a bearing on a shaft or within a housing. Broadly, the device includes a locking part disposed between first and second concentric members and biased into a frictional engagement with a first of the members so that when such member moves relative to the second member, the locking part is moved frictionally engaging the second member for locking the members together. In one form of the locking device a coil spring is wound about and frictionally engages a first member within a second member and has a tang engageable with a recess in the second member for interlocking the members responsive to rotation of the first member. Another embodiment of the locking device includes an arcuate-shaped spring having wedge portions engaging a first member within a recess of the second member. The recess of the second member is defined by eccentric arcuate locking surface portions converging toward the first member whereby the locking part is moved into wedging relationship between the first and second members for interlocking such members.

This is a divisional application of application Ser. No. 248,573, filedApr. 28, 1972, now U.S. Pat. No. 3,880,483.

This invention relates to locking devices and more particularly relatesto locking devices for interconnecting relatively movable concentricmembers. The locking device is particularly suited to the locking of abearing on a shaft or within a housing.

It is a well known practice to use ball and roller bearings forrotatably supporting shafts and similar mechanical structure from somemember of the apparatus involved. The shaft extends through an innerring comprising the inner race of a bearing while the outer race of thebearing is secured in any suitable structure such as a housing. It ispreferred that the inner race of the bearing and the shaft be lockedtogether in some manner and the outer race and the housing be connectedto minimize relative movement between the parts involved. The borethrough the inner race may be sized to effect an interference fit on theshaft. This approach, however, presents problems both in bearinginstallation and when bearing removal is necessary. Another method ofsecuring the inner race of a bearing on a shaft involves the use of acollar having an eccentric bore engageable with a mating eccentric outersurface on an end flange portion of the inner bearing race. A singleradial set screw locks the collar on the shaft so that relative rotationof the inner race in the collar tends to clamp the end of the inner raceagainst the shaft. Rotation in the other direction, however, tends toloosen the collar on the shaft. Another method which has been widelyused for securing an inner bearing race on a shaft is the use of atleast two radial set screws which engage the shaft to hold the innerrace against movement on the shaft.

The inertia of the inner ring or race of the bearing, and precessionresulting from radial clearance between the shaft and the base of theinner ring since it rotates with the shaft, causes the race to tend tolag relative to the shaft so that there are constant forces between theinner race and shaft which must be opposed by whatever means is employedfor connecting the race on the shaft. Both the collar method and the setscrew method of connecting the race on the shaft have seriousdeficiencies. Both approaches fix the center line of the inner ring atan angle to the center line of the shaft proportional to the totalradial clearance between the inner race bore and the shaft and inverselyproportional to the length of the inner race along the bore of the racein contact with the shaft. This angularity decreases the useful life ofthe bearing and shaft assembly. The tightening of set screws on theshaft mars the surface of the shaft making removal of the bearing overthe surface-damaged areas of the shaft difficult. The angularity or tiltbetween the inner race and the shaft tends to loosen the set screw orscrews employed. Generally, particularly with equipment which is used agreat deal, the bearings and shaft will eventually have to be replaceddue to the damage which occurs both to the shaft and the inner race ofthe bearing.

A recently devised system for fixing the inner race of a bearing on ashaft employs two wedges which are secured along internal recesses ofthe bore of the bearing inner race for movement along eccentric surfacesof the recesses into a wedging relationship between the inner race andthe shaft. The wedges comprise clips which extend radially around an endface of the inner race and longitudinally a short distance along theouter wall surface of the inner race so that a tool may engage the clipsfor forcing them into a wedging relationship between the shaft and theinner race. Such arrangement works reasonably well by effecting awedging relationship at two angularly spaced locations around the innerrace so that the shaft is forced against the inner race bore wall at athird location. Such system, however, has shortcomings including aninability to determine by visual inspection whether the inner race isproperly locked on the shaft, a flange end extension is required on theinner race, and the external portions of each of the two clips creates aconstant hazard as the race rotates with the shaft. The externalportions of the clip readily will become entangled with any materialswhich might touch the shaft and bearing assembly such as rags,operator's clothing, and the like. A positive action in setting ordriving the clips into wedging relationship is required to effectivelylock the inner race of the bearing on the shaft.

It is an object of the present invention to provide a locking device forinterconnecting two members.

It is another object of the invention to provide a locking device forinterconnecting relatively movable concentrically disposed members.

It is an especially important object of the invention to provide alocking device for connecting the inner race of a bearing on a shaft andthe outer race of the bearing within a housing.

It is another object of the invention to provide a bearing lockingdevice which minimizes tilt of the inner race of the bearing on a shaftand reduces shaft damage due to forces between the shaft and the bearingrace.

It is another object of the invention to provide a locking device forconnecting a bearing inner race on a shaft in a manner which causesengagement and tightening of the locking device responsive to therotational force between the shaft and the bearing race.

It is another object of the invention to provide a locking device forlocking a bearing inner race on a shaft against both rotational andaxial movement.

It is a still further object of the invention to provide a lockingdevice for connecting an inner race of a bearing on a shaft or the outerrace of the bearing in a housing which is locked without positiveexternal action or force.

It is another object of the invention to provide a locking device of thecharacter described which has no external protruding parts creatingsafety hazards.

It is another object of the invention to provide a locking device of thecharacter described which includes a coil spring to frictionally engageone of two members interconnected by the spring responsive to movementof the member.

It is another object of the invention to provide a locking device of thecharacter described which includes an arcuate spring part having wedgeportions disposed on the biased into frictional engagement with a firstof two members and movable by such member to a wedging relationshipbetween the first and a second member for frictionally engaging thesecond member to interlock the first and second members. In accordancewith the invention there is provided a locking device especially adaptedto locking inner races or rings of bearings on shafts and for lockingouter races or rings of such bearings within housings. Broadly, thelocking device includes a locking part biased to frictional engagementwith a first of two concentric relatively movable members for movementby the first member to a position at which the locking part engages thesecond of the members for locking the first and second members together.In one specific form of the locking device a coil spring is wound arounda shaft in frictional engagement with the shaft surface, the coil springhaving a cleat or tang extending into a recess within the second memberfor holding the spring against rotation within the second member.Rotation of the shaft tightens the spring on the shaft causing thespring to rotate with the shaft whereby the tang in the recess of thesurrounding bearing inner race effects engagement with and rotation ofthe bearing race, thereby coupling the shaft with the race in responseto rotation of the shaft. Various embodiments of the spring-type lockingdevice provide for holding the shaft against longitudinal or axialdisplacement responsive to a tightening of the spring on the shafteffected by a longitudinal force applied to the shaft tending to movethe shaft relative to the bearing inner race. In a further form of thespring locking device a pair of concentric springs are disposed aroundthe shaft within the inner race of the bearing providing a lock betweenthe shaft and the bearing which permits slight slippage between theshaft and the inner race as a safety feature which prevents springdamage under certain heavy load conditions. Still further forms oflocking devices embodying the invention include arcuate shaped springlocking parts biased into engagement with the shaft within an internalrecess of the inner race of a bearing, such recess being defined byeccentric arcuate locking surfaces causing a wedging of the locking partwhen the shaft rotates the locking part within the inner ringinterlocking the shaft and inner race. The locking is responsive toshaft rotation and does not require prior wedging or setting of thelocking part in the shaft and inner race. All forms of the lockingdevice include a fully enclosed locking part having no projectingportions tending to rotate and become entangled with loose material suchas rags and operator clothing.

The invention, together with its objects and advantages, will be morefully understood from the following detailed description taken inconjunction with the accompanying drawings wherein:

FIG. 1 is a side view in section and elevation of a typical ball bearinglocked on a shaft by a single spring between the shaft and the innerrace;

FIG. 2 is an enlarged view in section along the line 2--2 of FIG. 1;

FIG. 3 is a view in section and elevation along the line 3--3 of FIG. 2;

FIG. 4 is a top fragmentary plan view of a modified form of a lockingdevice using a single spring for both rotational and axial locking;

FIG. 5 is a fragmentary view in section along the line 5--5 of FIG. 4;

FIG. 6 is a fragmentary view in section and elevation along the line6--6 of FIG. 5;

FIG. 7 is a view in cross section of another form of locking deviceutilizing a single spring;

FIG. 8 is a view in section and elevation along the line 8--8 of FIG. 7;

FIG. 9 is a fragmentary side view in section and elevation showing thelocking of the outer race of a ball bearing within a housing inaccordance with the invention;

FIG. 10 is a fragmentary view in section and elevation along the line10--10 of FIG. 9;

FIG. 11 is a side view in section and elevation of a still further formof spring-type locking device embodying the invention for locking ashaft within the inner race of a ball bearing;

FIG. 12 is a view in section along the line 12--12 of FIG. 11;

FIG. 13 is a side view in elevation of the outer spring of the lockingdevice of FIG. 11;

FIG. 14 is an end view in elevation of the spring shown in FIG. 13;

FIG. 15 is a side view in elevation of the inner spring of the lockingdevice of FIG. 11;

FIG. 16 is an end view in elevation of the spring shown in FIG. 15;

FIG. 17 is a side view in elevation and section showing the inner raceof a ball bearing locked on a shaft in accordance with another form ofthe invention;

FIG. 18 is an enlarged view in section along the line 18--18 of FIG. 17;

FIG. 19 is a side view in section and elevation along the line 19--19 ofFIG. 18;

FIG. 20 is a view in section of a slightly modified form of the lockingdevice shown in FIGS. 17-19;

FIG. 21 is a side view in section and elevation along the line 21--21 ofFIG. 20;

FIG. 22 is a view in section of a still further modified form of lockingdevice embodying the invention for locking the inner race of a bearingon a shaft;

FIG. 23 is a view in section and elevation along the line 23--23 of FIG.22;

FIG. 24 is a view in section and elevation of another form of lockingdevice for locking the inner race of a bearing on a shaft in accordancewith the invention; FIG. 25 is a fragmentary side view in section andelevation showing the locking device of FIG. 24 in the inner race of aball bearing for locking the inner race on a shaft;

FIG. 26 is a fragmentary side view in section and elevation partiallybroken away showing a lower cental portion of the locking device ofFIGS. 24 and 25;

FIG. 27 is a view in cross section showing a further modified form oflocking device for securing the inner race of a bearing on a shaft;

FIG. 28 is a side view in section and elevation along the line 28--28 ofFIG. 27.

Referring to FIG. 1 of the drawings, a conventional ball bearingassembly 40 is shown locked on a shaft 41 in accordance with theinvention. The bearing includes an inner race 42, an outer race 43, aplurality of balls 44, and a cage 45 for holding the balls incircumferential spaced relationship around the annular space definedbetween the inner and outer races of the bearing. The bearing is sealedat opposite ends for holding lubricants in and dirt out by suitable sealassemblies 50 and 51.

In accordance with the invention, the bearing 40 is secured on the shaft41 by a coil spring 52 which locks the shaft 41 with the bearing innerrace 42. The spring 52 is preferably formed of rectangular wire wound toinclude a minimum of between two and three turns with opposite endsterminating in the vicinity of each other and provided with out-turnedtangs 53 and 54. The spring is wound to a normal relaxed diameterslightly less than the diameter of the shaft 41 so that when the springis wrapped around the shaft, as illustrated in FIG. 2, it frictionallygrips the shaft 41 and thus is biased into engagement with the shaft.The resiliency of the spring causes it to wrap down on the shaft. Thespring is disposed within an internal annular recess 55 in the innerrace 42 which opens into a radial slot 60 defined circumferentially byend faces 61 and 62 and extending axially, as seen in FIG. 1,substantially the thickness of the coil spring 52. Statedquantitatively, as evident in FIG. 1, the axial thickness of the slot 60is equal to approximately the cumulative thickness of five coils of thespring 52. As evident in FIGS. 2 and 3, the radial depth of the internalannular recess 35 in the inner race 42 is somewhat greater than thethickness of the wire forming the coil spring 52 so that the coils ofthe spring do not engage the inner ring with the spring coming incontact with the ring only along the tangs 53 and 54.

The locking device illustrated in FIGS. 1-3 functions to lock the innerring 42 on the shaft 41 irrespective of the direction of movement of theshaft. When the shaft rotates clockwise, as viewed in FIG. 2, the spring52 is rotated with the shaft until the tang 54 engages the lateralrecess end wall 62 within the inner ring. Since the spring issufficiently tight on the shaft to bias it into a frictionally engagingrelationship on the shaft as the shaft rotates clockwise and the springis held by the tang 54 engaging the surface 62, the spring tends tofurther tighten or wrap down on the shaft. This may be better recognizedby visualizing the spring, as seen in FIGS. 1 and 3, with the shaftrotating in a direction so that the upper portion of the shaft is movingtoward the observer. As the coils of the spring are frictionally engagedby the shaft surface, the spring tightens on the shaft more tightlygripping the shaft proportional to the relative force between the shaftand the inner race. As the force applied to the shaft increases, thespring wraps down tighter so that the shaft and the inner race are moresecurely coupled together. Irrespective of the relative force betweenthe shaft and the inner race, the shaft and race will remain securelylocked together unless such force exceeds the sheer strength of thespring 52 breaking the tang 54 from the spring. So long as the end ofthe spring at the tang 54 is held as described and the shaft is rotatedclockwise, the spring firmly grips the shaft locking the inner ring onthe shaft so that the ring rotates with the shaft. Subsequent to theengagement of the tang 54 with the surface 62 there is no slippagebetween the shaft and the inner ring. If the shaft is rotated in acounterclockwise direction, the spring turns with the shaft until thetang 53 engages the slot surface 61 of the inner ring so that the springwraps down in the opposite direction firmly gripping the shaft andinterlocking the shaft and inner ring.

The installation of the bearing 40 on the shaft 41 with the interlockingspring 52 is extremely simple. With the bearing off the shaft the springis manipulated into the recess 55 and the tangs 53 and 54 inserted intothe slot 60. After the spring is in the recess, the tangs 53 and 54 arespread apart by a suitable tool, such as a screwdriver, unwrapping orunwinding the spring to increase the diameter sufficiently to slide theshaft 41 through the bearing inner race and spring until the bearing isat the proper location along the shaft. The tool spreading the tangs isthen withdrawn allowing the spring to contract on the shaft. No otherinstallation steps are necessary. The spring effectively interlocks theshaft and bearing inner race for either direction of rotation of theshaft. The entire locking system is housed within the inner race withoutprojecting obstructions creating a safety hazard. The locking systemautomatically engages the shaft and bearing race without external actionor force such as driving of wedges into position or a similar positiveinstallation step. Rotation in either direction effects the sametightening of the spring gripping action with full engagement betweenthe entire periphery of the spring and the shaft irrespective of thedirection of rotation of the shaft. The inner race does not tilt to theextent of conventional locking devices. The spring tabs 53 and 54 act assafety features which will shear when an excessive load is applied,thereby avoiding serious damage to the equipment.

FIGS. 4, 5, and 6 illustrate a modified form of bearing inner racelocking device utilizing a single spring for locking the bearing andshaft both rotationally and axially. A bearing, not shown, of the natureillustrated in FIG. 1, has an inner race 70 somewhat longer than theinner race 42 shown in FIG. 1. The inner race 70 is locked with theshaft 41 by a spring 71 disposed around the shaft within an internalannular recess 72 of the inner race. The spring has a normal diameterslightly less than the diameter of the shaft so that it is biased intofrictional engagement with the shaft when in locking relationship on theshaft as shown in the drawings. The spring 71 has a pair of end tangs 73and 74 which hold the spring against both rotational and axial movement.The tang 73 projects radially outwardly into a lateral slot 75 in theinner race 70 opening into the internal recess 72 of the race.Similarly, the tang 74 extends radially outwardly into a recess 80formed in the inner race axially spaced from the slot 75. The spring 71functions to rotationally lock the race 70 on the shaft 41 in the samemanner as described with respect to the locking system illustrated inFIGS. 1-3. Clockwise rotation of the shaft, as viewed in FIGS. 4 and 5,causes the tang 74 to be rotated to the near edge surface of the slot 80holding the spring as it is wrapped down by its frictional engagement onthe shaft to tightly grip the shaft, thereby locking the ring 70 on theshaft during clockwise rotation. Similarly, counterclockwise rotation ofthe shaft 41 rotates the tang 73 to the near edge surface of the slot 75causing the spring to wrap down on the shaft, more tightly gripping theshaft and locking the inner bearing race with the shaft duringcounterclockwise rotation. A particular feature of the locking system ofFIGS. 4-6 resides in the holding of the shaft and inner race togetherresponsive to axial loads. An axial load applied to the shaft directedtoward the left, as seen in FIG. 6, causes the tang 73 of the spring toengage the slot face 75a holding the tang end of the spring againstaxial movement toward the left, while the force applied to the coils ofthe spring through the frictional engagement with the shaft causes thecoils to tend to decrease in diameter more tightly gripping the shaftholding the shaft against axial movement in the inner race. Similarly,movement of the shaft relative to the race toward the right in FIG. 6causes the tang 74 to engage the slot face 80a holding the tang end ofthe spring against axial movement to the right while the spring tends tostretch and thus decrease in diameter more tightly gripping the shaft tohold the shaft against axial movement toward the right. It is well knownthat a spring when stretched axially tends to decrease in diameter sothat the individual coils of the spring thus stretch longitudinally oraxially but contract radially or decrease effectively in diameter. Itwill be apparent that the axial spacing of the slots and the axialthickness of the slots must be such that the tang at the end of thespring from which the load is being applied is held against axialmovement while the tang at the opposite end of the spring may movesomewhat away from the holding slot to allow the spring to be stretchedaxially for contraction on the shaft. The greater the axial loadapplied, the more tightly the spring is wound down on the shaft. Thespring 71 is installed in the same manner as described with respect toFIGS. 1-3. After manipulating the spring into the recess 72 in the innerrace and inserting the tangs into the slots, the tangs may beeffectively spread apart to increase the effective diameter of thespring sufficiently for insertion of the shaft through the inner race.

FIGS. 7 and 8 illustrate a still further form of bearing lock employinga single spring to produce a dual spring effect. An inner race 90 of abearing similar to that shown in FIG. 1 has an end flange somewhatgreater in length than those of the previous embodiments. A spring 91 isdisposed between the shaft and the inner race in an internal annularrecess 92 within the inner race. The inner race also has an internalslot 93 opening into the recess 92 and located at the axial midpoint ofthe recess. The slot 93 is rectangular in shape having a long dimensionextending circumferentially perpendicular to the axis of the inner race.The spring 91 is provided with a central kink 91a formed in the middlecoil of the spring and extending outwardly for holding the springagainst rotation in the inner race. The kink 91a effectively divides thespring 91 into a first end portion or half 91b, and a second end portionor half 91c, each of which serves the function of an independent springdepending upon the direction of rotation and the direction of axialforces applied to the shaft. The kink serves the same function as theend rangs on the previously described locking springs. When the shaft 41is rotated in a clockwise direction relative to the inner race 90, asviewed in FIG. 7, the kink 91a holds the spring against rotation in theinner race while the frictional engagement between the shaft surface andthe spring rotates the spring with the shaft. The end portion 91c of thespring is tightened on the shaft causing that portion of the spring tomore securely grip the shaft locking the shaft with the inner race. Anaxial force applied to the shaft, as viewed in FIG. 8, toward the rightcauses the portion 91c of the spring to wrap down on the shaft holdingthe shaft against axial movement to the right relative to the innerrace. The kink 91a of the spring is held against the axial movement bythe right face of the slot 93 while the end portion 91c of the springtightens down on the shaft. Similarly, counterclockwise direction ofrotation of the shaft tightens the spring portion 91b, and an axialforce on the shaft toward the left, as seen in FIG. 8, tightens thespring portion 91b so that the shaft and inner race are locked togetheragainst both rotational and axial forces. The axial spacing between thespring turns, as shown in FIG. 8, has been found to increase the axialforce which may be applied between the shaft and the inner race.

FIGS. 9 and 10 illustrate the application of the invention to a lockingsystem for holding the outer race of a bearing within a housing. A ballbearing 100 of conventional design includes an inner race 101 secured onthe shaft 41 by any suitable means such as the various embodiments oflocking devices disclosed herein. The bearing has an outer race 102which is locked within an annular housing 103 by a coil spring 104. Thespring has end tangs 105 and 110 which project radially outwardly fromthe spring coils into an internal recess 111 formed in the housing 103opening inwardly into an internal annular recess 112 in which the coilsof the spring are disposed. The outer race is held against axialmovement in the housing in a direction toward the left, as seen in FIG.9, by a snap ring 113 fitting in aligned recesses of the bearing outerrace and the inner face or bore surface of the housing. Rotation of theshaft and bearing in either direction tends to rotate the outer race ofthe bearing which is locked against such rotation within the housing bythe spring 104. The spring is wound to a diameter slightly less than theouter diameter of the race 102 so that the spring is biased intofrictional engagement with the race and is tightened further on the raceby rotation of the race relative to the housing. Clockwise rotation ofthe shaft 41, as viewed in FIG. 10, tends to turn the outer race 102 tocause the tang 110 of the spring to engage the right face of the recess111 holding the spring against further rotation and effecting a wrappingdown or tightening of the coils of the spring on the bearing outer race,thereby interlocking the outer race and the housing. Similarly, rotationof the shaft and bearing in a counterclockwise direction causes the tang105 to engage the recess surface effecting a wrapping down of the springcoils to hold the bearing outer race against counterclockwise rotationwithin the housing. The only slippage between the outer race and thehousing is the circumferential movement permitted by the width of therecess or slot 111 and the positions of the tangs within the slot.

FIGS. 11-16 illustrate the application of the spring principle to abearing locking system employing a pair of concentrically disposedsprings between the shaft and a bearing inner race. Referring to FIG.11, a ball bearing 120 has an inner race 121 secured on the shaft 41 byconcentrically disposed outer and inner springs 122 and 123. The springsare positioned within an internal annular recess 124 of the bearinginner race 121. The outer spring 122 has opposite ends turned axially toform end tangs at 122a and 122b extending in opposite axial directions.The tangs are aligned axially within the cylindrical surfaces defined bythe coils of the spring. The spring is wound to a diameter which formsan interference fit within the internal annular recess 124 of thebearing inner race 121. The inner spring 123 is provided with end tangs123a and 123b, both of which are turned radially outwardly as best seenin FIG. 16. The inner spring is wound to a diameter which forms aninterference fit on the shaft 41.

When the shaft 41 is rotated, one of the inner spring tangs engages oneof the tangs on the outer spring causing the inner spring to wrap downon the shaft and tending to unwind the outer spring causing expansionwithin the recess 124 to effect a tighter engagement with the inner raceof the bearing. Specifically, if the shaft is rotated in a clockwisedirection, as viewed from the left end of the shaft in FIG. 11, the tang123a of the inner spring engages the axial tang 122a of the outerspring. The frictional engagement of the spring with the shaft causesthe inner spring to wrap down on the shaft so that the spring rotateswith and is frictionally locked to the shaft. The force applied fromtang 123a of the inner spring to the tang 122a of the outer springunwinds the outer spring which is in interference fit relationshipwithin the recess 124 of the bearing inner ring 121. The unwinding ofthe outer spring expands the spring within the recess 124 gripping thebearing inner race 121 so that the shaft is locked with the bearinginner race by means of the inner spring 123 and the outer spring 122.Similarly, counterclockwise rotation of the shaft 41 turns the innerspring 123 with the shaft until the end tang 123b of the inner springengages the axially extending end tang 122b on the outer spring. Theresistance to the rotation of the inner spring provided by theengagement of the tang 123b with the tang 122b causes the shaft 41 towind the inner spring down more tightly gripping the shaft and causingthe co-engaging tangs to tend to unwind the outer spring so that it moretightly grips the bearing inner race within the recess 124 coupling theshaft and inner race through the concentric springs responsive to thecounterclockwise rotation of the shaft 41. The dual spring arrangementis particularly suitable for use under heavy load, low speed rotationconditions where the shaft tends to slip relative to the inner race. Theouter spring tends to slip slightly within the inner race of the bearingso that loads which normally would shear the tang from one of thesprings will not effect such a result in the dual spring locking system.Thus, a safety factor is inherent in the use of the concentric springson heavy load applications.

Referring to FIGS. 17-19, a ball bearing 120 having an inner race 121 isinterlocked with a shaft 41 by an arcuate spring locking part 122. Theinner race has an end flange 123 provided with an internal recess 124and a radial slot 125 opening through the race into the internal recess124. The recess 124 is slightly longer measured axially than the widthof the spring locking part 122, as evident in FIGS. 17 and 19, and isdefined by an eccentric locking surface of circular shape formed on acenter located below the axis of the bore 121a through the inner race,as seen in FIG. 18, so that when the shaft is disposed through the innerrace, the annular space 124 narrows toward the slot 125. Thus, therecess 124 has neck or radially narrow portions 124a and 124b on eitherside of the slot. The locking part 122 is a spring member formed of aslender strip having a central loop 122a, side arcuate portions 122b and122c, and inwardly bent end wedge portions 122d and 122e. The overallconfiguration of the locking part 122 is a partial circular shape formedon a radius slightly less than the radius of the shaft 41 so that whenthe locking part is within the recess 124 between the inner race and theshaft, the part is biased against the shaft frictionally engaging theshaft surface.

The locking system shown in FIGS. 17-19 interlocks the bearing innerrace and the shaft responsive to rotation of the shaft in eitherdirection. Viewing the locking system as seen in FIG. 18, when the shaftis rotated clockwise, the biasing of the spring locking part against theshaft causes the shaft to rotate the locking part with the shaft untilthe part wedges between the shaft and the inner race locking surfacelocking the shaft and inner race together. The locking part is carriedwith the shaft until the wedge end 122d is moved into a wedgingrelationship in the recess neck 124b where the wedge end is lodgedtightly between the shaft and the inner race frictionally locking theinner race on the shaft. Reversal of the shaft to rotate the shaft in acounterclockwise direction causes the shaft to carry the locking partwith it counterclockwise disengaging the wedge end portion 122d frombetween the shaft and the inner race while rotating the outer wedge endportion 122e of the locking part into the recess neck 124b where thewedge end is jammed tightly between the shaft and the inner race lockingthe shaft and inner race together. Thus, the inner race is locked withthe shaft in either direction responsive to shaft rotation. At any timerelease of the inner race from the shaft is desired the central loop122a of the locking part is depressed manually by a suitable tool suchas a screw driver so that the end wedges of the locking part are movedfarther into the recess 124 to wider portions of the recess at which thewedges are essentially free of the surfaces of the shaft and the innerrace permitting disengagement of the inner race from the shaft. Thebiasing of the spring type locking part against the shaft surfacepermits the shaft to rotate the locking part into wedging relationshipwith either direction of shaft rotation without an initial setting ofthe wedge ends of the part in locking positions as required by presentlyknown bearing locking systems.

The bearing locking system of FIGS. 20 and 21 is identical to that shownin FIGS. 17-19 in all respects except that the internal recess in theinner race is defined by two eccentric surfaces formed on separatespaced centers. Referring to FIG. 20 a bearing inner race 121a having aslot 125 is provided with an internal recess 130 defined by twosemicircular eccentric surfaces 130a and 130b generated about centerswhich are spaced on opposite sides of the axis of the center of the bore127a through the inner race 126 of the bearing. As viewed in FIG. 20 thecenter of the surface 130a is spaced along a horizontal line extendingthrough the axis of the bore 127a spaced to the right of the axis whilethe center of the eccentric surface 130b is along the same horizontalline to the left of the axis of the inner race bore. The outer surfaceof the shaft 41 and the eccentric recess surfaces define narrow neckportions 130c and 130d, respectively, to permit the wedge ends 122e and122d to move into locking relationship along the shaft surface withinthe inner race recess. The locking system shown in FIGS. 21 and 20operates in precisely the same manner as that of FIGS. 17-19 so thatrotation of the shaft 41 in either direction couples the bearing innerrace with the shaft.

The bearing locking system of FIGS. 22 and 23 includes a bearing innerrace 140 having a side slot 141 opening into an internal annular recess142 defined by a circular locking surface generated about an axisaligned with and spaced above the axis of the bore 140a of the innerrace so that a restricted area or space 142a is defined along the lowercentral portion of the shaft 41 when disposed through the bearing innerrace. A spring locking part 143 is positioned within the recess 142 ofthe inner race around the shaft 41. The locking part extendsapproximately 270° around the shaft and includes a central loop 143aprojecting into the inner race slot 141 and side arcuate portions 143band 143c. The locking part has end wedge inwardly turned portions 143dand 143e which move into locking or wedging relationship between theshaft and the bearing inner race responsive to the direction of rotationof the shaft. The locking part is formed on a radius slightly less thanthe radius of the shaft so that when the shaft extends through the partthe locking part is biased against the outer surface of the shaft. Whenthe shaft rotates clockwise as seen in FIG. 22 the wedge end 143e isrotated into the restricted recess area 142a between the shaft and thebearing inner race locking the shaft and inner race together.Counterclockwise rotation of the shaft moves the wedge end 143d of thelocking part into the restricted recess area 142a locking the shaft andbearing inner race together. For releasing the shaft from the innerrace, the locking part 143 is lifted by grasping the loop 143a with asuitable tool retracting the end wedges 143d and 143e to positionspermitting the shaft to be easily withdrawn from the bearing race.Similarly, in assembling the shaft and bearing race, the locking part ismaneuvered into recess 142 of the race and then lifted by means of thecentral loop 143a to allow the shaft to be inserted through the innerrace and locking part.

A still further form of bearing locking system is shown in FIGS. 24, 25and 26. Referring to FIG. 25, a ball bearing 150 having an inner race151 is secured on a shaft 152 by an arcuate three lobe locking part 153.The locking part comprises a ring-like segment which extendsapproximately 330° around the shaft including three wedge lobe sections153a, 153b, and 153c spaced approximately 120° apart. The wedges 153aand 153b are interconnected by a narrow arcuate section 153d of lessradial thickness than the thickness of the wedge lobes. Similarly, thelobes 153b and 153c are connected by integral section 153e. The two freeends of the wedge member are effectively tapered by external edgereverse curve surfaces 153f and 153g. Similar surfaces bound thejunctions of the wedge segments 153a, 153b and 153c with theintermediate integral connecting portions 153d and 153e so that thethree wedge lobes are symetrical circular segments of the integrallocking part.

The locking part 153 is disposed within a recess 154 provided within theinner bearing race 151 and defined by three eccentric locking surfaces154a, 154b, and 154c. The locking surfaces each is a cylindrical surfacegenerated about an axis spaced toward the surface from the axis of thebore 151a through the bearing inner race and has a radius less than theradius of the bore of the inner race. The locking surfaces are spaced at120° intervals and each extends 120° around the bearing inner race. Theradii of the three eccentric surfaces are equal and are of a lengthwhich with the off center positioning of the axis lines of the surfacesproduce the narrow space sections 154d, 154e, and 154f. The threelocking part wedge lobes 153a, 153b, and 153c each disposed along one ofthe eccentric surfaces 154a, 154b, and 154c, respectively. The innerdiameter of the locking part 153 is slightly less than the diameter ofthe shaft 152 and the wedge lock is disposed in a shallow externalannular groove 160 of the shaft. The locking part is biased intoengagement with the shaft surface around the groove 160. The groove 160permits locking relative to thrust loads but is not required forrotational locking.

The locking part 153 is illustrated in FIG. 24 in a neutral position atwhich each of the wedge lobes is at the center of an eccentric lockingsurface. Upon rotation of the shaft in either direction, the lockingpart is rotated by the shaft until the three wedge segments each ismoved into a wedging relationship within the recess 154 between theinner bearing race and the shaft. If the shaft is rotated in a clockwisedirection, the wedge lobe 153a is rotated toward the narrow recess space154d until the lobe is tightly engaged between the locking surface 154aand the shaft surface. Similarly, the wedge lobe 153b is moved into alocking relationship between the shaft and the inner race toward thenarrow space portion 154e and the wedge lobe 153c is moved toward thenarrow space 154f. Rotation of the shaft in a counterclockwise directionrotates the locking part with the shaft until the three wedge lobes arein locking engagement between the shaft along the three eccentriclocking surfaces. The only slippage which occurs between the ring andthe shaft is that permitted by the movement of the inner race and shaftuntil the wedge segments are in locking positions between the shaft andthe race. The use of the three lobe locking part 153 providessubstantial frictional engagement between the locking wedges of the partand the internal surface of the bearing inner race and substantialengagement between the locking part and the surface of the shaft 152which minimizes any tendency to damage the shaft or the inner bearingrace. The inner race of the bearing is counterbored at 151b leading intothe recess 154 to facilitate the installation of the locking part in therace and to admit a suitable tool through the counter bore between theshaft and the inner race for slightly spreading the locking part byengagement of its free end to release the shaft from the locking part.

Another form of locking system for interconnecting the inner race of abearing with a shaft is illustrated in FIGS. 27 and 28. A bearing innerrace 160 is locked with a shaft 161 by a pair of resilient arcuatelocking parts 162 and 163. The locking parts are disposed in an internalrecess 164 provided in the inner race 160 communicating with a slot 165through which the locking parts may be manipulated for release of thebearing from the shaft. The two locking parts 162 and 163 are positionedin circumferential overlapping relationship arranged axially side byside as seen in FIG. 28. The recess 164 of the inner race is basicallyan annular recess of uniform depth including enlarged locking surfaceportions 164a, 164b, and 164c circumferentially spaced at 120° apartaround the inner race. The locking surfaces of the inner race recess areprovided to accommodate wedging lobes on the two locking parts forwedging the lobes between the shaft surface and the locking surfaces tolock the inner race and shaft together during rotation in eitherdirection of the shaft. The locking part 162 has a bent end portion 162awhich engages one side of the recess 165 for manipulating the lockingpart when releasing the shaft and the bearing. The locking part 162additionally has three arcuate outwardly extending wedge lobes 162b,162c and 162d which are spaced at 120° intervals to correlate with thepositions of the arcuate enlargements of the inner recess of the bearinginner race. The wedge lobes on the part 162 are positioned to providewedging action during clockwise rotation of the shaft as viewed in FIG.27 and thus are biased against the recess locking surfaces towards whichthe member is rotated when the shaft turns clockwise. The lobe 162d ofthe part 162 comprises in end of the part and as shown is disposed inthe recess portion 164a. Similarly, the locking part 163 has a bent endportion 163a and circumferentially spaced wedge lobes 163b, 163c and163d, reading clockwise in FIG. 27. The other end of the part 163 isformed by the wedge lobe 163d which is disposed in the recessenlargement 164c. The wedge lobes of the part 163 are positioned so thatthey effect wedging action when the shaft 161 rotates counterclockwisein the inner race. The two locking parts are positioned side by sidearound the shaft within a shallow external annular recess 170 of theshaft. The inner race 160 of the bearing is counter bored at 171 tofacilitate installation of the locking parts in the race. With both ofthe locking parts installed between the inner race and the shaft, thewedge lobe on one of the parts bears against the recess locking surfacesat first sides of the enlarged recess portions of the inner race whilethe wedge lobes of the other locking part each bear against the oppositeside locking surfaces of the enlarged recess portions of the inner race.By so positioning the locking parts backlash between the shaft and theinner race is essentially eliminated as the wedge lobes on each part aredisposed to essentially immediately wedge into locking positionsresponsive to shaft rotation in either direction. When release of theshaft from the bearing inner race is desired, a suitable tool such as ascrew driver may be inserted into the slot 165 between the ends 162a and163a of the locking parts. Applying circumferential forces to the twoend loop end portions of the locking parts forces the locking partssurrounding the shaft in opposite directions towards the centralportions of the recess portions 164a, 164b and 164c at which the wedgelobes do not bear tightly in wedging relationship against the shaft andthe locking surfaces of the recess of the bearing inner race releasingthe shaft and inner race from interlocked relationship.

In the various locking systems illustrated and described each bearinghas been shown locked at one end only of the bearing inner race. Withsuch a locking arrangement the tilt of the inner race is essentially cutin half as contrasted with normal conventional bearing locking systems.If desired, the bearing inner race may be extended on the opposite sideof the bearing with a locking system installed in such extension so thatthe bearing inner race is locked at both ends of the bearing. Such anarrangement in terms of the system shown in FIGS. 24-26 would include anextension on the opposite side of the bearing inner race 151 includingan inner recess corresponding to the recess 160 and the installation ofa second locking part 153 in such recess so that the bearing inner raceis locked by a pair of locking parts disposed at opposite ends of theinner race. This arrangement would essentially eliminate tilt of thebearing on the shaft. In each form of the system illustrated anddescribed, the particular locking part employed is biased to africtionally engaging relationship with one of the members being lockedtogether while being movable by such member to a locking relationshipwith the other of the members responsive to relative movement betweenthe members. More specifically, in bearing applications the locking partis biased to frictional engagement with the shaft going through abearing and movable by shaft rotation relative to the inner race of thebearing to a position of interlocking relationship between the shaft andsuch bearing inner race. None of the locking systems require initialsetting or locking of the shaft with the bearing inner race but aredynamically activated by shaft rotation to effect the desired locking.Bearing and shaft damage is essentially eliminated and part replacement,often required in conventional bearing locking devices, is thus alsominimized, if not eliminated. In each of the locking systems the use ofprojecting part portions is not required and thus the locking systemsrender the bearings and shaft much safer. While certain forms of theinvention show multiple locking lobes and eccentric locking surface, itwill be recognized that more lobes may be used than illustrated andequal spacing is not essential. Also, in forms such as illustrated inFIGS. 24-26 showing three lobes a single lobe and corresponding lockingsurfaces are operable though not to be preferred.

What is claimed and desired to be secured by Letters Patent is:
 1. Alocking system for coupling two concentric relatively moveable memberstogether responsive to a force applied to one of said memberscomprising: a first member; a second member concentrically disposedabout said first member, said second member having an internal recessextending about said first member and a slot opening into said internalrecess; and a locking part biased to frictional engagement with saidfirst member comprising a coil spring wound about said first member andhaving a tang portion in the form of a central kink disposed in saidslot in said second member for engaging said second member and aplurality of coils on each side of said central kink, the coils on oneside gripping said first member responsive to a first direction ofrotation of one of said members and the coils on the other side grippingsaid first member responsive to rotation of said one of said
 2. Alocking system for coupling two concentric relatively moveable memberstogether responsive to a force applied to one of said memberscomprising: a first member; a second member concentrically disposedabout said first member; a locking part comprising a spring memberextending circumferentially partially around said first member andbiased to frictional engagement with said first member; said lockingpart including locking wedge portions at opposite free ends of saidpart, said second member being provided with an internal recess definedby an eccentric locking surface generated about at least one axis spacedfrom the axis of said first member, the surface of said first member andsaid eccentric surface of said second member defining a space includinglocking surface portions around said first member having a radialdimension varying from a maximum greater than the radial dimension ofeach of said wedge portions of said locking part to a minimum less thanthe radial dimension of said wedge portions, said wedge portions of saidlocking part being positioned on opposite sides of said minimumdimension portion of said internal recess whereby relative movement ofsaid members moves one of said wedge portions to a locking positionagainst one of said locking surface portions.
 3. A bearing lockingdevice for locking an inner race of a bearing on a shaft comprising:means providing an internal annular recess within said inner race ofsaid bearing; and locking means comprising a coil spring within saidrecess of said inner race around at least a portion of said shaft, saidlocking means being biased into frictional engagement with said shaftand being movable by rotation of said shaft to a position between saidshaft and said race for interlocking said shaft and said race.
 4. Abearing locking system in accordance with claim 3 wherein said bearinginner race has a circumferentially extending slot opening into saidannular recess and said locking means comprises a coil spring wound to adiameter less than the diameter of said shaft and having end tangsextending outwardly from the coils of said spring into said slot, saidspring wrapping down on said shaft responsive to rotation of said shafteffecting engagement of one of said end tangs with a side face of saidslot whereby said shaft and said inner race are interlocked by saidspring responsive to rotation of said shaft in either direction.
 5. Abearing locking system in accordance with claim 3 wherein said lockingmeans comprises a coil spring wound to a diameter less than the diameterof said shaft and having end tangs turned outwardly from the coils ofsaid spring, and said bearing inner race being provided with two axiallyspaced slots opening into said recess of said race, said end tangs onsaid springs each extending into a separate one of said slots wherebysaid spring wraps down on said shaft for interlocking said shaft andsaid bearing inner race both axially and circumferentially responsive torotation of said shaft in either direction and application of an axialforce to said shaft in either axial direction.
 6. A bearing lockingsystem in accordance with claim 3 wherein said locking means comprises acoil spring having a plurality of coils, one of said coils near thelongitudinal center of said spring having an outwardly extending loop,and said bearing inner race having a slot opening into said recess ofsaid race, said spring loop being disposed in said slot for holding saidspring against rotation in either direction in said inner race, saidspring being wound to a diameter less than the diameter of said shaftand being adapted to wrap down on said shaft responsive to rotation ofsaid shaft in either direction whereby said spring grips said shaft andsaid loop on said spring holds said spring against rotation interlockingsaid shaft with said inner race.
 7. A bearing locking assembly inaccordance with claim 3 wherein said locking means comprises a firstinner coil spring wound to a diameter less than the diameter of saidshaft and disposed on said shaft in alignment with said recess in saidinner race of said bearing and having radially outwardly extending endtangs, a second outer coil spring disposed concentrically around saidinner spring and having axially extending end tangs aligned to beengaged by said end tangs of said inner spring responsive to rotation ofsaid inner spring within said outer spring, said outer spring beingwound to a diameter greater than the diameter of said inner spring andgreater than the inside diameter of said recess of said bearing innerrace, said inner spring being adapted to wrap down on said shaftresponsive to shaft rotation whereby an end tang on said inner springengages an end tang on said outer spring and said outer spring isadapted to unwind to grip said bearing inner race within said recesswhereby said inner and outer springs couple said shaft with said innerrace responsive to rotation of said shaft in either direction.
 8. Abearing locking assembly in accordance with claim 3 wherein said recessof said inner race is defined by an eccentric circumferential lockingsurface within said inner race providing a recess varying in radialdepth from a minimum along one circumferential portion of said recess,and said locking means comprises an arcuate spring locking partextending within said recess around less than 180° of said shaft andhaving locking wedge lobes along opposite end portions thereof, saidlocking part being positioned within said inner race around said shaftat a location at which the central portion of said part between saidwedge lobes extends through the portion of said recess of minimum depthand said locking wedge lobes are on opposite sides of said portion ofsaid recess of minimum depth, said wedge lobes being greater in radialdimension than the depth of said minimum recess portion whereby rotationof said shaft in either direction moves one of said wedge lobes into awedging relationship between said locking surfaces of said bearing innerrace recess and said shaft.